CN86210682U - Centrifugal pump - Google Patents

Centrifugal pump Download PDF

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Publication number
CN86210682U
CN86210682U CN 86210682 CN86210682U CN86210682U CN 86210682 U CN86210682 U CN 86210682U CN 86210682 CN86210682 CN 86210682 CN 86210682 U CN86210682 U CN 86210682U CN 86210682 U CN86210682 U CN 86210682U
Authority
CN
China
Prior art keywords
blade
impeller
centrifugal pump
pump
back shroud
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
CN 86210682
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Chinese (zh)
Inventor
刘殿魁
何本元
崔永强
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Institute of Engineering Thermophysics of CAS
Original Assignee
Institute of Engineering Thermophysics of CAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Institute of Engineering Thermophysics of CAS filed Critical Institute of Engineering Thermophysics of CAS
Priority to CN 86210682 priority Critical patent/CN86210682U/en
Publication of CN86210682U publication Critical patent/CN86210682U/en
Expired - Lifetime legal-status Critical Current

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Abstract

The utility model discloses a centrifugal pump, which relates to the improvement of the centrifugal pump impeller. According to the ternary flow theory, the result of the flow velocity distribution on the at least 25 streamlines in the pump is analyzed, and the flow passage shape of the pump impeller with high hydraulic efficiency can be designed. The centrifugal pump concretely contains the increase of the axial length of the impeller blade; the ternary twisted blade of the axial entry section is formed; the curvature radius of the meridian plane line of the impeller passage can be enlarged; the short blades in the passage of the adjacent long blades adopt the asymmetric arrangement, and the blades of the impeller outlet are designed to be a retracting form, etc. The pump efficiency of the utility model which is no lower than 75-78% exceeds the existing mechanical industrial part criteria of China, and the performance of the centrifugal pump is equivalent to the foreign like advanced products.

Description

Centrifugal pump
The utility model is a kind of centrifugal pump, is specifically related to the improvement of this centrifugal pump impeller structure.
Adopt the monobasic flow theory in the centrifugal pump design at present mostly, only analyze in the pump runner flowing on center streamline (press the passage section equalization), the molded lines that carries out impeller channel in view of the above designs unreasonable, thereby pump efficiency is not high.
The purpose of this utility model is exactly to improve the molded lines design of centrifugal pump impeller, improves the efficient of pump.
In order to realize goal of the invention of the present utility model, the three-dimensional flow theory of turbomachines that we set up according to China scientist professor Wu Zhonghua, analyze in the pump velocity flow profile at least 25 streamlines, design the high pump impeller flow channel shape of hydraulic efficiency, its concrete technical measures comprise: increase the ternary twisted blade that impeller blade axial length and formation comprise the axial entrance section, increase impeller passage meridian surface shape radius of curvature, short blade in adjacent linear leaf passage adopts asymmetric layout, and the impeller outlet Blade Design becomes the retraction form.
Describe summary of the invention of the present utility model and embodiment in detail below in conjunction with accompanying drawing.
The utility model centrifugal pump impeller as shown in Figure 1, comprise following a few part: the front shroud (1) of seal ring before having, back shroud (3), 6-12 between front shroud and back shroud ternary twisted blade (2), the axle sleeve (6) that links to each other with back shroud, have keyway, back sealing flange (4), impeller balance hole (5).The implication of the used symbol of accompanying drawing 1 mark impeller structural dimensions is:
φ R---impeller diameter
The outlet diameter of φ B---blade,
φ 1---the import external diameter of blade,
φ 0---the import internal diameter of blade,
A---impeller outlet width,
B---blade axial length.
Compare with the like product of prior art, the utility model impeller has following feature:
1. the blade axial length B has increased 40-100% than the prior art like product, blade axial length B and impeller inlet external diameter φ 1Ratio B/ φ 1>0.5.The blade always flow path direction incremental portion of extending is the ternary distorted shape.
This improved advantage is: the growth of (1) blade, the diffusion gradient of minimizing impeller inner fluid reduces the flow separation loss.(2) greatly reduce the flow velocity of fluid in blade inlet.More since blade import distorted shape according to the Theory of Three-dimensional Flowing precise design, the import impact loss is little, the blade suction surface flow velocity is low, thereby the efficient height of pump and anti-cavitation performance are good.
2. the meridian surface shape that intersects of blade and front shroud and back shroud is as the solid line f of accompanying drawing 2 1f 2And b 1b 2Shown in, the meridian surface shape of prior art blade is in the figure with dotted line f 1' f 2' and b 1' b 2' expression.Among the figure 0,1,2 ... 12 numerals such as grade are in order to expression design-calculated passage section sequence number.The utility model requires f 1f 2And b 1b 2Than f in the prior art 1' f 2' and b 1' b 2' the radius of curvature of respective points big.Particularly at the middle part of blade passage m sAnd m hNear, with the middle part m of prior art blade passage s' and m hNear ' comparison, the radius of curvature difference of meridian surface shape is particularly outstanding, and the utility model blade middle part meridian surface shape raises up regulation: meridian surface shape f 1f 2And b 1b 2Radius of curvature R in any point 0With impeller inlet external diameter φ 1Ratio R 0/ φ 1>0.35.
Above-mentioned improvement is to do the ternary computational analysis according to the fluid in the impeller is flowed to draw, and improved structure makes the interior flow velocity trend of runner evenly, has reduced the secondary flow loss that flows.
Also can adopt the impeller of linear leaf and short blade intercross arrangement according to the utility model, as shown in Figure 3, short blade (2s) but is partial to the linear leaf of wheel rotation direction one side not on the geometric center lines of runner between two adjacent linear leafs (2L).ω and garden arc arrow represent that impeller is the clockwise direction rotation among Fig. 3.In the utility model, short blade (2s) is than the geometric midline position (2s ') between two linear leafs (2L) (being the position of prior art short blade), is Δ θ to the angle of sense of rotation ω deflection, the utility model regulation Δ θ=7 °-15 °.
According to the Theory of Three-dimensional Flowing analysis, this layout of the utility model will reduce fluid in the loss of incidence of short blade import leading edge and the blending loss in impeller outlet downstream.Experimental test shows that this improvement can make pump efficiency improve 1-2% than the prior art product.
According to another remodeling of the present utility model be, the outlet blade of impeller has adopted " retraction " structure, and as shown in Figure 1, promptly blade (2) outlet diameter φ B is less than impeller diameter φ R.The length of the utility model suggestion retraction is advisable with the 2-5 millimeter, and promptly blade exit diameter phi B is than the little 4-10 millimeter of impeller diameter φ R.Test shows, this structure that blade is shortened, not only not can as tell about in the textbook can lower efficiency like that, can also make pump efficiency improve 1-2% sometimes.
The reason that " retraction " outlet blade structure improves pump efficiency is: blade (2) prescinds, and front shroud (1) and back shroud (3) keep original outside diameter constant, blade " retraction " is arrived within front shroud and the back shroud, form as the B of the φ among Fig. 1<φ R, make fluid after flowing out blade passage, still be subjected to the constraint of front shroud and back shroud, reduced fluid and entered the preceding diffuses flow loss of draining spiral case (not drawing among Fig. 1), thereby pump efficiency is improved.
Description of drawings:
Fig. 1. the composition of centrifugal pump impeller and structural dimensions.
Fig. 2. impeller blade is in the projection of meridian plane.Solid line is represented the utility model among the figure, and dotted line is then represented the common form of prior art product.
Fig. 3. the layout of the short blade between two linear leafs.(2s) is the short blade in the utility model impeller among the figure, and (2s ') then represents the common form of prior art product.
The embodiment of the utility model centrifugal pump and effect thereof can be used accompanying drawing 1-accompanying drawing 3 and table 1 explanation.
As shown in Figure 1, present embodiment:
Impeller diameter φ R=180 millimeter,
Blade exit diameter phi B=176 millimeter,
Blade import external diameter φ 1=80 millimeters
Blade import internal diameter φ 0=34 millimeters,
Impeller outlet width A=10 millimeter,
Blade axial length B=45 millimeter,
Blade axial length B and blade import external diameter φ 1Ratio B/ φ 1=0.5625.
As shown in Figure 2, along the increase direction (being the flow direction of fluid in pump impeller) of designing and calculating passage section sequence number from 0 to 12, present embodiment blade (2) and the crossing meridian surface shape f of front shroud (1) 1f 2, with the crossing meridian surface shape b of back shroud (3) 1b 2, slope all is dull increasing.Curve f 1f 2And b 1b 2Do not combine (the molded lines f in the prior art by garden arc and straightway 1' f 2' with b 1' b 2' be mostly that each adds one section straightway by one section garden arc and constitutes).
Curve f 1f 2Minimum profile curvature radius be 36 millimeters, with impeller inlet external diameter φ 1Ratio be 0.45.Curve b 1b 2Minimum profile curvature radius be 65 millimeters, with impeller inlet external diameter φ 1Ratio be 0.8125.
The scheme of linear leaf of present embodiment (2L) and short blade (2s) intercross arrangement as shown in Figure 3.Each 5 of linear leaf, short blades, the ratio of short blade inlet diameter φ s and impeller diameter φ R is φ s/ φ R=0.475, short blade and geometrical center position deflection angle Δ θ=9 °.
Present embodiment is a kind of single suction, single-stage horizontal centrifugal pump, and experiment measuring shows to have energy-efficient characteristics, and its technical performance is as follows:
The design discharge point:
Flow Q=50 cubic meter/hour
Lift H=43.5 rice
Efficiency eta=79%
Cavitation performance NPSH=2.1 rice
Best efficiency point:
Flow Q=66 cubic meter/hour
Lift H=41.5 rice
Efficiency eta=82.8%
Cavitation performance NPSH=3.3 rice
The present embodiment centrifugal pump surpasses the centrifugal pump sample data of the current standard JB3559-84 of China Ministry of Machine-Building Industry set quota and more external company's same traffic in the performance of design discharge point, and its contrast is as shown in the table:
Table 1. the utility model pump and home and abroad like product performance comparison

Claims (4)

1, a kind of centrifugal pump that comprises impeller and volute, the blade wheel structure of this pump particularly, impeller has front shroud [1], back shroud [3], the blade [2] between between front shroud and the back shroud of seal ring before the band, the axle sleeve that has keyway [6] that links to each other with back shroud, afterwards sealing flange [4] and impeller balance hole [5], its impeller blade is the ternary blade profile, and feature of the present utility model is:
(1) blade [2] axial length B and impeller inlet external diameter φ 1Ratio greater than 0.5 (B/ φ 1>0.5),
(2) blade [2] and front shroud [1] and the crossing meridian surface shape f of back shroud [3] 1f 2And b 1b 2Radius of curvature R in any point oWith impeller inlet external diameter φ 1Ratio greater than 0.4 (R o/ φ 1>0.4).
2, centrifugal pump as claimed in claim 1 is characterized in that impeller blade adopts linear leaf and short blade intercross arrangement, and short blade (2s) is partial to the linear leaf (2L) of wheel rotation direction one side, and the angle △ θ of its deflection is 7 °-15 °.
3, centrifugal pump as claimed in claim 1 or 2 is characterized in that blade exit diameter phi B less than impeller diameter φ R, and φ R and the φ B scope of differing are the 4-10 millimeters.
4, a kind of centrifugal pump that comprises impeller and volute, the blade wheel structure of this pump particularly, impeller has front shroud (1), back shroud (3), the blade (2) between between front shroud and the back shroud of seal ring before the band, the axle sleeve that has keyway (6) that links to each other with back shroud, afterwards sealing flange (4) and impeller balance hole (5), its impeller blade is the ternary blade profile, the feature of the utility model centrifugal pump is: impeller diameter φ R=180 millimeter, blade exit diameter phi B=176 millimeter, impeller inlet external diameter φ 1=80 millimeters, blade axial length B=45 millimeter, blade axial length B and impeller inlet external diameter φ 1Ratio be 0.563, the meridian surface shape f that blade and front shroud and back shroud intersect 1f 2And b 1b 2Minimum profile curvature radius R 0=36 millimeters, minimum profile curvature radius R 0With the ratio of impeller inlet external diameter be 0.45.
CN 86210682 1986-12-29 1986-12-29 Centrifugal pump Expired - Lifetime CN86210682U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN 86210682 CN86210682U (en) 1986-12-29 1986-12-29 Centrifugal pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN 86210682 CN86210682U (en) 1986-12-29 1986-12-29 Centrifugal pump

Publications (1)

Publication Number Publication Date
CN86210682U true CN86210682U (en) 1987-10-07

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN 86210682 Expired - Lifetime CN86210682U (en) 1986-12-29 1986-12-29 Centrifugal pump

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Country Link
CN (1) CN86210682U (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100363627C (en) * 2004-11-17 2008-01-23 深圳市兴日生实业有限公司 Automatic rotating electric water pump according to correct direction
CN101970883A (en) * 2008-03-10 2011-02-09 曼柴油机和涡轮机欧洲股份公司 Cover disk for a closed impeller
CN101718282B (en) * 2009-11-26 2011-04-13 浙江工业大学 Centrifugal pump
CN102182703A (en) * 2011-05-09 2011-09-14 中国石油大学(华东) Efficient non-plugging discontinuous impeller of vane pump
CN102251982A (en) * 2010-05-20 2011-11-23 上海置本节能环保技术工程有限公司 Full three-dimensional method for reforming energy-saving technology of water pump
CN103423168A (en) * 2013-07-24 2013-12-04 大连理工大学 Hydraulic model of AP1000 filter screen back-flushing pump
CN106762807A (en) * 2017-02-28 2017-05-31 杭州大路实业有限公司 A kind of low-specific-speed centrifugal compound impeller and its method for designing
CN107448412A (en) * 2016-06-01 2017-12-08 株式会社久保田 Impeller
CN107448413A (en) * 2016-06-01 2017-12-08 株式会社久保田 Impeller

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100363627C (en) * 2004-11-17 2008-01-23 深圳市兴日生实业有限公司 Automatic rotating electric water pump according to correct direction
CN101970883A (en) * 2008-03-10 2011-02-09 曼柴油机和涡轮机欧洲股份公司 Cover disk for a closed impeller
CN101970883B (en) * 2008-03-10 2013-12-25 曼柴油机和涡轮机欧洲股份公司 Cover disk for closed impeller
CN101718282B (en) * 2009-11-26 2011-04-13 浙江工业大学 Centrifugal pump
CN102251982A (en) * 2010-05-20 2011-11-23 上海置本节能环保技术工程有限公司 Full three-dimensional method for reforming energy-saving technology of water pump
CN102182703A (en) * 2011-05-09 2011-09-14 中国石油大学(华东) Efficient non-plugging discontinuous impeller of vane pump
CN102182703B (en) * 2011-05-09 2015-12-09 中国石油大学(华东) A kind of discontinuous impeller of vane pump without blocking
CN103423168A (en) * 2013-07-24 2013-12-04 大连理工大学 Hydraulic model of AP1000 filter screen back-flushing pump
CN103423168B (en) * 2013-07-24 2015-10-14 大连理工大学 A kind of hydraulic model of AP1000 filter screen backwashing pump
CN107448412A (en) * 2016-06-01 2017-12-08 株式会社久保田 Impeller
CN107448413A (en) * 2016-06-01 2017-12-08 株式会社久保田 Impeller
CN106762807A (en) * 2017-02-28 2017-05-31 杭州大路实业有限公司 A kind of low-specific-speed centrifugal compound impeller and its method for designing

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